Universal relieving machine



Oct. 21. 1924. 1,512,631 F. MULLER 1 UNIVERSAL RELIEVING MACHINE Filed April 1921 Q 7 Sheets-$heet 1 Oct. 21. 1924.

F. MULLER UNIVERSAL REIJI EVING MACHINE Filed April 22. 1921 '7 Sheets-Sheet 2 F. MULLER UNIVERSAL RELIEVING MACHINE Oct. 21, 1924.

7' Sheets-Sheet 5 Filed p il 22. 1921 MQQ Oct. 21, 1924.

F. MULLER UNIVERSAL RELIEVING MACHINE Filed April 22. 1921 7 Sheets-Sheet 4 QQN a u QM N ii!!! IIiIIl A v Wm run-n...

Oct. 21. 1924. a 1,512,631

F. MULLER UNIVERSAL RELIEVING MACHINE Filed April 22 1921 7 Sheets-Sheet 5 Oct. 21, 1924. H

F. MULLER UNIVERSAL RELIEVING MACHINE Filed April 22 1921 '7 sheets-Sheet 6 OcL'Zl. 1924. 1,512,631

F. MULLER UNIVERSAL RELIEVING MACHINE Filed April 22 1921 7 Sheets-Sham 7 reamed 0a. 21, 1924.

* UNITED STATES PATENT OFFICE.-

FRIEDERICH IULLER, 0F HARTFORD, CONNECTICUT, ASSIGNOR TO PRATT a WHIT- NEY COMPANY, OF NEW YORK, N. Y., A CORPORATION OF NEW JERSEY.

UNIVERSAL RELIEVING MACHINE.

Application filed April 22, 1921. Serial No. 468,541.

T9 all whom it may concern:

Be it known that I, FRIEDERIGH MiiLLER, a citizen of the United States, residing at Hartford, in the county of Hartford and State of Connecticut, have invented certain new and useful Improvements in Universal Relieving Machines, of. which the following is a specification. i

This invention relates to lathes and particularly to relieving lathes adapted to perform relieving operations on reamers, taps, milling cutters, counterbores and other metal working cutters. However, the machine is not limited for use upon cutters of the kinds mentioned and can be used in practically all cases in which relievin movements of the cutting tool are require For the sake of convenience the term cutters is used throughout the specification, but it will be understood that the term is intended to include not only. rotary metal working tools but also any other articles for which relief is required.

In many respects the machine illustrated herein is like that illustrated and described in my Reissue Patent No. 15,127, dated July 19, 1921. The principal object of the invention is to provide certain improved mechanism particularly adapted for usewith the machine illustrated in such patent.

One obi'ect of the invention is the provision of improved mechanism for increasing the driving speed range of the tool carriage operating screw. I perform this ob ject by providing two separate driving mediums for the screw, one being preferably ope-rated from the spindle and the other from a shaft operated at a rapid speed relative to the spindle.

Another object of the invention is the provision of. an indexing means in combination with the improved mechanism for increasing the driving speed range of the tool carriage operating screw, whereby either the carriage operating screw or the work spindle, which elements are ordinarily connected together and o erated in synchronism, may be given a de nite indexing movement independent of and. relative to the other, such" movements serving to move the tool along the work or to rotate the work without moving the other member. 1 1

Another object of the-invention is to provide means for readily disengaging the work spindle from the tool operating shaft and for operating either of these elements independently of the other, such operation being necessary to bring the tool and cutter into the proper relative position at the beginning of a cutting operation.

Another object of the invention is the provision of improved mechanism whereby the extent of the feeding movement of the tool is limited and the tool feed thereby stopped at any desired point. I 1

Another object of the invention is to provide a machine combining a tool feeding mechanism and 'a compensating mechanism adapted respectively to operate on milling cutters or hobs having annularly arranged teeth thereon and on spiral hobs, means being provided for rendering either of such mechanisms operative or inoperative.

Another object of the invention resides in the provision of an improved tool-supporting mechanism which may be adjusted to any one of a plurality of relatively angular positions whereby the tool ma be made to face in the direction most a apted to the particular work to be performed.

Other and more specific objects 'of the invention will become apparent from the followi specification taken in connection with ilie accompanying drawings. It should be understood, however, that the improvements illustrated herein are not necessarily limited to the details shown on the drawings or to use in a machine as illustrated, the scope of the invention being defined inthe claims appended hereto.

Referring to the figures of the drawin Figure 1 is a side elevation of the entire machine.

Fig. 2 is a side elevation of the upper portion of the machine, certain of the parts being shown in section.

Fig. 3 is a left end elevation. Fig.4: is a right end elevation. Fig. 5 is a vertical transverse sectional view taken on the line 5-5 of Fig. 2.

Fig. is a detail view of the structure shown in Figs. 8 and 9.

Fi 11 is a detail sectional view taken on the line 1111 of Fig. 3.

Fig. 12 is a fragmentar plan view of the right hand end of the mac ine, showing pan ticularly the gearing and shafts operated thereby.

Fig. 13 is a side elevation of the same.

Fig. 14 is a fragmentary detail sectional view of a portion of the mechanism illustrated in Figs. 12 and 13.

Fig. 15 is a plan view of the tool-supportin carriage.

ig. 16 1S3, sideelevation thereof, the tool support and the machine bed being shown in .section.

Fig. 17 is a vertical longitudinal section through the same on the line 1717 of Fig. 15, the tool-sup orting block being removed.

Fig. 18 is a pan view of the tool support.

Fig. 19 is a vertical transverse sectional view taken on the line 19-19 ofFig. 15.

Fig. 20' is a vertical transverse sectional view through the tool support on the line 20-20 of igs. 16 and 18.

Fig. 21 is a vertical transverse sectional view taken on the line 21--21 of Fig. 15, the tool carriage bein shown in elevation.

Fig. 22 is an e arged horizontal sectional view of a.portion of the tool carriage taken on the line 22-22 of Figs. 23 and 24.

Fig. 23 is a vertical transverse sectional view thereof taken on the line 23-23 of Fig. 22.

ig. 24 is a front elevation thereof.

Fig. 25 is a detail sectional view taken on the lme 2525 of Fig. 24.

Referring to the drawings, 1 represents the main base or bed upon which the other .parts of the machine are mounted. Means are provided for holding and rotatin a cutte-r to be relieved, this means preferabl prising a headstock 2 and a tailstock 3, each provided with a center. stood, however, that the invention in its broader phases is not limited to the particular construction shown,and that the cutter may, if preferred, be otherwise held, as for instance by a chuck or collet.

The headstock is provided with a framecasting 4 rigidly secured to the bed. This casting is rovided with suitable bearings 5 and 6 in which there is rotatably mounted a live spindle 7, which preferably carries a center 8 and a face plate 9. v Loosely mounted on the spindle 7' are two worm wheels 10 and 11. Preferably, as indicated, particularly in my aforesaid patent, the teeth of the worm wheel 10 are adapted to mesh with a double-threaded worm, and the teeth of the worm wheel 11 are adapted to mesh with a single-threaded worm. Extending transversely of the headstock and mounted in suitable hearings in the casting 4,

and 11.

com- It will be under-' is a drive shaft 12 provided at its rear end with a driving means, here shown in the form of a set of cone belt pulleys 13. Secured on the drive shaft 12, preferably adjacent the belt pulleys, is a pinion 1 1 which meshes with pinions 15 and 16 mounted respectively on suitably mounted transverse shafts 17 and 18. Mounted respectively on the shafts 17 and 18 are worms 19 and 20 which mesh respectively with the aforesaid worm wheels 10 When the worm wheels are constructed as already described, the worm 19 is provided with a double thread and the worm 20 with a single thread. It will be seen that the construction issuch that when the worms 19 and 20 are rotated the worm wheels will be given different rotative speeds, the wheel 10 1n this case having a speai considerably in excess of that of the wheel 11. I preferably mount the belt pulley 13 loose on the shaft 12 and provide a friction clutch 21 between the pulley and the pinion 14. The clutch may be shifted into and out of driving engagement by means of a handle 22 mounted on a shaft 23. Rotation of the handle moves a lug 24 along a stationa cam slot in the headstock whereby the sha t 23 and a clutch-engaging arm 25 thereon are moved longitudinally of the shaft and the clutch is moved into and out of frictional engagement with the driving sleeve 26 (Fig. 6).

Splined tothe spindle between the worm wheels 10 and 11 is a clutch element 27 having teeth at each side adapted r ctively to mesh with similar teeth form on the worm wheels. It will be seen that by means of this clutch element either of the worm wheels can be operatively connected with the spindle.

For moving the clutch element 27 longitudinally of the spindle, there is provided an oscil atory lever 28 provided with pins or projections fitting in a circumferential groove in the clutch element. The lever 28 is secured to a transverse rock shaft 29 provided with an operating lever 30. It will be seen that by means of the lever 30 the clutch element 27 can be controlled-so as to be maintained in neutral position as shown in Fig. 2, or moved into engagement with either of the worm wheels 10 or 11. The lever 30 is provided with a spring-pressed pin 31 adapted to enter suitable holes in the casting 4 and thus lock the lever and the clutch element in the desired position.

The tailstock 3 is so mounted that it does not interfere in any way with the o eration of the reciprocating tool-carrying slide. As illustrated, there is provided a horizontal supporting bar 32 which is parallel with firmounted on the bar for adjustment there' along, a clamp operated by a handle 36 be ing adapted to secure the same in its adjusted position. The sleeve 37 and center 38 can be moved longitudinally by means of the usual screw 39 and hand wheel 40 and can be clamped in work-supporting position by means of a nut 41. vFor a more detailed description of this mechanism reference should. be made to my aforesaid patent.

It will be seen that by suitably positioningthe tailstock on the bar 32 and by then adjusting the center 38! by means of the sleeve 37 and the hand wheel 40, a cutter or other article to be relieved can be secured in the usual way between the two centers 8 and 38; and the cutter can be connected to the face plate on the headstock spindle in any usual ,or preferred way to be rotated.

It may in some cases, however, be desirable to mount the cutter entirely on the spindle and for this purpose a collet mechanism. such as shown and described in my aforesaid patent may be provided. In such case the tailstock mechamsm may be entirely removed if desired.

The cutting tool must be so held and supported that it can be moved toward and from the cutter to be relieved in timed relation to the rotation thereof. The tool must make as many movements forward and backward during eachv cutter rotation as the cutter has teeth in each annular convolution thereon. A cutting tool is indicated at 42, and for supporting it there is provided a reciprocable horizontal slide 43 to which the tool is secured in any suitable way. A

supporting device 44 is rovided for the slide 43 and preferably this supporting device is provided with separated parallel ways with which the slide eng es. When it is desired to make it possible or the cutting tool to approach the cutter from any angle, the supporting device 44 must be in the form of a turntable rotatable about a vertical axis, and in the drawings the supporting device 44'is so shown. The turntable 44 rests upon a saddle 45 which is supported on the bed of the machine. The turntable is'provided with annular bearing surfaces which fit similar bearing surfaces formed on the saddle, and the saddle is also provided with an annular T-slot 46 into which extend T-bolts 47 adapted to lock the turntable in any desired angular position. Preferably the saddle 45 is slidable along the bed 1, the bed being provided with the usual ways on which the saddle rests; By

by a suitable cam 51. When the or turntable 44 is a. lever 50 having two arms, one of which has connection with the slide 43 and the other of which is engaged supporting device 44 is in the form ofa turntable, as here shown, the cam 51 is positioned centrally with its axis coincident with the axis of the turntable, thus making it possible for the cam and lever to properly cooperate with the turntable in any position of adjustment. Preferably the cam is in the form of a groove in the top of a wheel 52. The wheel 52 is mounted on a conical stud 53 secured to a depressed part of the saddle 45. The wheel 52 is preferably provided with worm teeth 54 which mesh with a worm 55 on a shaft 56. When the saddle 45 is adapted for longitudinal movement along the bed, the shaft 56 is longitudinally arranged and the worm 55 is splined to it. It will be clear that when the shaft 56 is rotated motion will be transmitted through the worm and worm wheel to rotate the cam.

One arm of the lever 50 is provided with a roller 57 which extends into the cam groove 51. The groove is preferably of the form shown in Fig. 15, being adapted to move the lever slowly in one direction and rapidly in the other. Connected with the slide 43 for normal movement in unison therewith, is a device 58 to which power is applied by the lever for actuating the slide. The lever 50 is adjustable so as to vary the amount of movement which it transmits to the device 58 and to the tool-carrying slide 43. Preferably this adjustment is effected by changing the effective length of one arm of the lever and, as shown, this arm of the lever is constructed with two telescopically engaging parts. At the sides of the body part of the lever are two slidable plates 59,

59 formed with oppositely disposed thickened portions 60, 60, each with a surface in the form of a section of a cylinder, these two cylindrical surfaces having a common center. The surfaces of the enlargements 60, 60 fit between transverse parallel surfaces 61, 61 provided on the actuating device 58, and as the surfaces on the parts 60, 60 are cylindrical, the engagement with the surfaces 61, 61 is maintained notwithstanding any angular movement. The two plates 59, 59 are secured to a block 62 which is'centrally recessed to receive anextension 63 on the body part of the lever. An adjusting screw 64 extends throughjan aperture in the block and is held against longitudinal movement with respect thereto. The inner end of the screw extends into a threaded aperture in the said extension 63. The outer end of the.

ilates 59, 59 can be moved so as faces 60, 60 toward or away from the pivotal center of the lever. Preferabl at the extreme inner position the center the cylindrical surfaces coincides with the pivotal 5 center, and no movement of the actuating device or the slide takes place as the lever is oscillated. As the screw is turned to move the center of the cylindrical surfaces outward, the movement of the actuating device and slide is gradually started and this move ment is increased as the effective length of the lever is increased. In this way the extent of movement of the tool slide can be varied from zero to maximum. The screw 64 can be clamped by means of the screw 65. While the cam 51 acts positively in both directions, I nevertheless prefer to provide a spring for assisting the cam in effecting the short rapid return movement of the slide whereby I avoid excessive strain on the lever, the cam and the several power transmitting parts. As illustrated, the turntable 44 is provided with an aperture 66 parallel with the line of movement of the actuating device and slide, and a spring 68 is provided which abuts at one end against the actuating device 58 and at the other end against a plug 69 threaded into the aperture 66. For holding the spring 68 in place there are provided pins 67 and 67 secured respectively to the actuating device 58 and to the plug 69.

As already stated, the cam wheel 52 is rotated by means of the shaft 56 and the worm 55. The shaft 56 is rotated synchronously with the spindle rotation through mechanism now to be described. This mechanism comprises a relatively high speed shaft 70 driven with the spindle op- L crating pinions 15 and 16 from the pinion 14 through idler gears 71, 72 and 73 to a gear 74 keyed to a short transverse shaft 75. This shaft carries a bevel gear 7 6"meshing with a'bevel gear 77 on the shaft 70. It should here be noted that the gear 72 is secured to a longitudinally movable shaft 78 adapted to be shifted longitudinally and rotated by means of a hand wheel 79. A spring-pressed latch 80 is adapted to engage in either of two annular grooves 81 in the shaft to secure the shaft in either of its two longitudinal positions. As illustrated in Fig. 5, the gear 72 is in engagement with both of its companion gears 71 and 73. When the shaft is moved longitudinally to engage the latch 80 in the other groove 81 the gear 72 will be disengaged from the gear 71 but will still be in engagement with the wider gear 73. When in such position the spindle may be given a rotary adjustment independent of the tool support by means of the hand wheel 82 and the tool support may be given a lateral movement toward or from the work independently of 55 the spindle by means of the hand wheel 7 9.

Such relative operation between the work and tool is necessary before beginning the cut in order to accurately position the tool relative to the teeth on the cutter.

Referring particularly to Fi s. 4, 12, 13

and 14, it will be seen that t e shaft drives the shaft 56 through a differential gearing 83, hereinafter more fully described and termed the compensating mechanism, to a shaft 84 in alignment with the shaft 70 and from a gear 85 on the shaft 84 throu h change speed gearing 86 to a gear 87 on t e shaft 56. As has already been stated, it is necessary for the cutting tool to make one forward and backward movement for each tooth of the cutter to be relieved. It is therefore necessary that for each revolution of the live spindle the cam 51 be given as many rotations as the cutter has teeth in each annular convolution thereon. By using gears 86 of the proper sizes the number of rotations of the cam for each rotation of the live spindle can be varied, and a further variation can be obtained by connecting one or the other of the worm wheels 10 or 11 with the live spindle, thus varying v the speed of the spindle with respect to the speed of the drive shaft 12. By means of this two-speed worm and wheel drive mechanism for the spindle, I am enabled to greatly increase the range of the machine without providing an unduly largenumber of interchangeab e gears.

As already stated, the carriage is preferably movable longitudinally of the bed and this movement can be effected either manually or by power. For the purpose of moving the carriage manually there is rovided a rack 88 secured to the bed. 8onnected with the saddle 45 is the apron 89 on which is mounted a short transverse shaft carrying a pinion 90 meshin with the rack. By means of a hand whee 91 and intermediate gears the pinion can be turned to move the carriage.

The power means for operating the carriage comprises a screw 92 operated through change speed gearing at the forward end of the machine. This mechanism is shown particularly in Figs. 2 and 3 wherein the screw is illustrated as being driven from the spindle. The gearin comprises a gear 93 secured to the spind e 7 and adapted to mesh either with a gear 94 or an idler pinion 95. The gear 94 and the idler inion 95 are mounted on a swinging brac et 96 adapted to be controlled by the hand lever 97. By means'of this lever the bracket 96 can be moved either to bring the gear 94 into mesh with the gear 93 as shown in Fi 3 or to bring the i ler inion 95 intomes with the gear 93, or to ring both the gear and .the pinion out of mesh. From the gear 94 power is transmitted to the lead screw through the gears 98, 99, 100, 101, 101' and a screw 115 or otherwise.

102, somev of which are interchangeable in the usual way to vary the rate of rotation of the lead screw with respect to that of the spindle. It will be seen that the lead screw can be entirely disconnected from the spindle or can be connected therewith for rotation in either direction. 103 illustrates a split nut mounted on the carriage and adapted to be engaged with and disengaged from the screw 92 by means of the usual cam mechanism 104 operated by a handle 105.

It will be seen that through the mechanism just described the tool carriage may be moved longitudinally of the spindle synchronously with the rotation of the spindle, such movement of the carriage being necessary when operating on a cutter having its teeth arranged with alead similar to a screw thread. When operating on a multiple start cutter it is necessary to rotate the spindle and cutter a definite'accurate amount independent of the movement of the tool carriage in order to bring each start into a definite position relative to the tool. For example, after finishing the cutting operation on one start of a two-start cutter or hob, the cutter must be rotated through 180 inde endent of any movement of the tool longitudinally of the cutter axis in order to bring the beginning of the second start into the proper cutting position 'relative to the tool. This operation may be performed by an indexing mechanism illustrated in Figs. 2, 3, 8, 9 and 10 andcomprising broadly two parts 106 and 107 connected to the screw operating shaft 109 and the spindle 7 respectively. As illustrated in Figs. 8, 9 and 10, the gear 99 is keyed to a sleeve 108 loosely mounted on the shaft 109 which sleeve has a flange 110 at the end opposite the gear 99. The flange 110 is notched at diametrically opposite points 111 to receive therein lugs 112 of the part 107. The part 106 is keyed to the shaft 109 and has a flange provided with a plurality of equally spaced notches 113 into any one of which isadapted to be rdceived a latch or lug 114 secured to the part 107 by means of It will be seen that by removing the latch 114 the two parts may be given any relative adjustment whereby the spindle is indexed relative to the tool. As illustrated, the relative size of the gears is preferablysuch that the angular movement given to the spindle corresponds to the angular movement of the or pitch the carriage screw 92 is necessarily.

indexing mechanism or shaft 109, the spindle bein given one rotation for each rotation of s aft 109.

In operating on cutters having a fine lead rotated very slowly to likewise move the tool slowly longitudinally of the cutter rela-. tive to the spindle rotation, while operating on cutters having a coarse lead the screw 92 must be rotated rapidly relative to the spindle rotation. The change speed gearing from thespindle to the screw, illustrated in Figs. 2 and 3, provide such a variation within certain limits. However, in order to increase the speed range of the screw, I provide the following mechanism. In Figs. 2 and 11 is shown a shaft responding to the shaft 109 and having loosely mounted thereon a sleeve 108'. A gear 99' is keyed to the sleeve and meshes with a gear 116 secured to the high speed shaft 70. The outer end of shafts 109 and 109' are identical and either is adapted to receive thereon the indexing? mechanism 106 and 107 and gear 100, the bushing 117 shown on the shaft 109' of course It will be seen, therefore, that the screw may be given a variety of relatively slow'rotative speeds from the spindle or a variety of relatively faster speeds from the high speed shaft 70. As stated above,.the gearing between the shaft 109 and the spindle is preferably one to one ratio. The connection between the shaft 109" and the spindle is preferably in the ratio often to one, that is, the tool carriage may be given a feeding movement from the shaft 109 ten times as fast as from the shaft 109. The change speed gearing between each of these shafts and the screw permits of a wide variation of feeds between and beyond these limits. The indexing mechanism is operated in the same manner on either shaft 109 or 109'.

The cutting tool 42 can be mounted on the slide 43 in any suitable manner. However, when the slide is mounted as herein shown and described, I prefer'a tool hold ing and supporting means which comprises a plate 118 adjustable angularly with respect to the slide and also longitudinally of the slide. The plate 118 is connected with a plate 119 having an annular beveled surface. A ring 120 having a similar beveled. surface surrounds the plate 119 and is. adjustably secured to the slide by means of bolts 121 engaging T-slots 122. This construction permits the plate'118 to be moved longitudinally of the slide or angularly, and when the bolts 121 are tightened the late is locked in place. Mounted on the ate 118 is a slide 123 horizontally mova le under the control of a screw 124. Mounted verticallyon the slide 123 are a plurality, four being illustrated, of bolts 125. A tool-supportin member 126 is provided with a plurality 0 holes therein for receiving the bolts 125 the bolts and holes being symmetrically arranged wliereby the support may be mounted on the slide in any one of four relatively ri ht angular positions. The tool may be afjusted by means of. a screw 127 and a strap 128 is adapted to secure the tool in place by means of two of the bolts 125. By means Oi th 091. mounting adjustment the 109' corbeing removable. I

tool may be made to face in the direction most adapted to the particular work to be performed and the tool holder may be so mounted that the tool 0st operating screw 124, as well as the other tool controls, is located in the most convenient position for the operator. This adjustable mounting is particularly useful in end relieving and relieving operations wherein the tool must operate from the side of the work opposite to that illustrated. In end relieving with a tool having a lateral cutting edge thereon, it is desirable to adjust the tool carriage to a right angular position with the feed screw 124 parallel with the work spindle while leaving the tool in a right angular position relative to the spindle. The improved adjustable tool support provides for such an adjustment since the tool holder 126 may be given a quarter turn to permit this relative relation of the parts. It will also be seen that by properly adjusting the tool support the screw 124 may be made to extend in a direction convenient to the operator as well as avoiding the engagement of the headstock 4 by the end 124 of the screw when operating with the tool on the side of the work opposite to that illustrated.

Means are provided whereby the extent of the forward movements of the cutting tool may be increased as the cutter rotates, thus efiecting feeding and causing the tool to take a fresh chip at each rotation of the cutter.

I prefer to effect the feeding automatically and preferably the construction is such that the feedin end of each gradually.

The actuating device 58 has been described as normally movable in unison with the tool carrying slide 43. The two elements are connected by a rotatable screw 129 which has threaded engagement with the slide. The inner end of the screw extends through an aperture in the actuating device and is held against longitudinal movement with respect to the said device by means of lock nuts at 130. Mounted in the device which supports the slide 43 (in this case the turntable 44) is a short rotatable shaft 131 provided at its inner end with a clutch element 132 which is shaped to engage the end of the clutch element 133 on the screw 129 and impart rotary movement thereto. It will be understood that the clutch elements permit relative longitudinal movement, thus permitting the actuating device and the slide to reciprocate without however causing any reciprocation of the screw actuating shaft 131.

Feeding is effected by turning the shaft 131 and this is preferably accomplished automatically. Loosely mounted on the shaft is a worm wheel 134 with which meshes a worm 135. Splined to the shaft 131- is a disk 136 and interposed between the disk and the rotation of the cutter instead of takes place intermittently at the.

worm wheel is a friction washer. Springs are provided for causing frictional engagement at the washer, thus providing a frictional connection between the Worm wheel and the shaft.

The devices for rotating the worm 135 may vary with the type of machine, but in a machine of the sort illustrated, in which the slide 43 is nounte'd on a turntable, the following elements are preferably provided for operating the Worm. As shown in Fig. 23, the worm 135 is secured to a horizontal shaft 137 mounted in suitable bearings in the turntable 44. At one end of the shaft 137 is a bevel gear 138 meshing with a bevel pinion 139 secured to a vertical bushing 140. This bushing carries at its lower end a toothed clutch element 141 upon which is rotatably mounted a gear 142. Slidably and rotatably mounted in the bushing 140 is a shaft 143 to the lower end of which is secured a ratchet wheel 144 having on its upper surface teeth adapted to mesh with the teeth of the clutch element 141. At the upper end of the shaft 143 is a grooved collar 145 into the groove of which fit projections on the forked arm of a bell-crank 146. By moving the bell-crank by means of the handle shown in Fig. 25, the shaft 143 can be raised or lowered to bring the clutch teeth on the ratchet wheel 144 into or out of engagement with the teeth on the clutch element 141. Mounted on the gear 142 is a ratchet or pawl 147 spring-pressed into en gagement with the teeth of the ratchet wheel 144. By means of this pawl the ratchet wheel is rotated in the clockwise direction whenever the gear is rotated in the said direction and this motion is transmitted to the sleeve 140 and the parts connected therewith whenever the ratchet wheel'is in its upper position to engage the clutch teeth.

Mounted on the turntable 44 for movement about the axis thereof, is a suitable power transmitting element, and by preference this element is in the form of an annular toothed ring 148. As shown, the ring 148 is mounted in an annular rabbet formed. at the periphery of the turntable. the bottom of the ring engaging the top surface of the saddle 45. The ring is provided with teeth on its outer periphery, and the construction of the turntable is such that these teeth are exposed throughout the major portion of the periphery. Means are provided for imparting movement to the ring 148, and this movement is transmitted to the gear wheel 142 by means of idler gears 149 and 150 mounted on the turntable. Inasmuch as the ring is concentrically mounted, the power connectionwith the said gear 142 is maintained for all positions of the turntable. For imparting movement to the ring 148 there is preferably provided a gear wheel 151 meshing with gear teeth cut on the under side of the ring (Fig. 2). It should be understood that the ring is freely rotatably mounted in the turntable and that the periphdral teeth thereon and the teeth in the under side thereof extend only a portion of the distance around the ring, such distance being suflicient, however, for all feeding operations. As more clearly illustrated in Fig. 16, the gear 151 is driven through the gears 152, 153 and 154, the gear 154 being splined to the longitudinal feed shaft 155.

The shaft 155 is mounted in suitable bearings in the bed and is provided at one end with means for imparting movement thereto. Preferably the shaft is given an oscillatory .movement and the means (Figs. 2, 3 and 7) for imparting such movement, as shown, comprises an arm 156 secured to the end of the shaft and oscillated by a link 157 Pivotally mounted on the headstock casting is a bell-crank 158, one arm of which is provided with a T-slot. A T-bolt 159 fits in the T-slot and serves as a pivot for the upper end of the rod 157. This pivot is adjustable along the arm and the amount of travel of the link as the bell-crank is oscillated can be varied from zero to maximum. Mounted on the live spindle 7 is a disk 160 provided with a cam groove 161. A roller on the bell-crank 158 fits this groove and the groove is so shaped that in at least one di-' rection the bell-crank isgiven a rapid movement.

From the foregoing description it will be seen that as the live spindle is rotated the cam 161, imparts a rocking movement to the bell-crank 158, which serves to reciprocate to a greater or less extent the link 157. By means of the link and arm, oscillatory movement is transmitted to the shaft 155 and through the connections described, this movement is transmitted to the gear 142. By means of the pawl 147 the movement of the gear 142 in one direction is' transmitted to the ratchet wheel 144, the pawl passing freely over the teeth of the ratchet wheel when the gear 142 moves in the other direction. When the ratchet wheel is connected with the sleeve 140 the intermittent movement thereof is transmitted to the worm wheel 134 from which, by means of the friction devices described, 1t is trans- .mitted to the shaft 131 and the feedscrew 129. As the movement in one direction occurs once for each revolution of the spindle and of the cutter driven thereby, the feed is effected once for each revolution of the cutter. The amount of feed at each revolution can be varied b adjustin the pivot at 159. It will be evi ent that t is automatic feeding mechanism is ordinarily used in relieving milling cutters or hobs having the cutting teeth arranged annularly thereon. When relieving a spiral hob this feeding mechanism will ordinarily be thrown, out of action.

In addition to the automatic feeding means, I preferably also provide hand operated means for controlling the tool. As illustrated, this hand controlled means comprises a hand wheel 162 mounted on a short shaft 163 on which is mounted a spiral gear 164 meshing with a spiral gear 165 on the shaft 137. Frequently in order to start the cutting it is desirable to advance the tool in the feeding direction at a speed greater than that caused by the automatic mechanism. This can be done at any time bymeans of the hand wheel without interfering in any way with the operative relation of the automatic mechanism. The ratchet wheel is advanced with respect to its driving pawl, the teeth of the wheel freely slipping under the pawl. Whenever the more rapid manual movement is discontinued, the movement by means of the pawl is resumed as before. In case it is desired to move the tool backward the ratchet wheel is disconnected by means of the bell-crank 146, thus placing the tool entirely under the control of the hand wheel.

For automatic feeding it .is preferable to provide means whereby the feeding is automatically stopped at a predetermined limit. My improved stop mechanism provided herein is most clearly shown in Figs. 22, 23 and 24. I provide a stop 166 on the outer face of a disk secured to the disk memher 136. I provide a second stop 167 adjustable in the path of movement of the first stop, such second stop preferably be ing mounted on the member 168 loosely mounted on the disk member 136. As a means for rotatably adjusting the member 168, I provide a worm 169 meshing with worm teeth 170 on the said member. The worm shaft extends outwardly of the easing and is provided with a knob 171 for rotating the same. An index dial 172 is secured to the shaft whereby the member 168, and therefore the stop 167, may be accurately set to stop the feedat the desired point. By suitably adjusting thestop 167 with respect to the stop 166 the latter engages the former and is'stopped thereby after feeding has taken place to the desired extent. It will be seen that as the first stop engages the second stop, further movement of the shaft 131 and of the feed screw is prevented, the friction elements permitting the worm to continue to turn as before. v

When the tool is to be controlled manually, it is desirable to revent the engagement of the stops. I or this purpose a spring-pressed 1atch 172 engages the stop 167 whereby the stopmay be held out of the path of movement of the stop 166 when desired. A handle 173 (Fig. 25) is provided on the shaft 17 4 for operating the bell-crank 146 to disengage the clutch element 141. A spring-pressed detent 175 within the handle serves to hold the clutch in either of its two positions.

In addition to forming part'of the automatic stop mechanism the friction elements described also serve to prevent injury to wherein the cutting edge of each of the several teeth along any one flute is in the same angular position on the cutter, the angular starting position of the tool relative tothe cutteris the same for each successive tooth along any one flute. However, when operating on a cutter or hob having its flutes cut spirally therein and the cutting edg ,of each successive tooth along any one flute therefore being arranged spirally around the cutter, it will be seen that the angular starting position of the tool relative to the cutter is slightly in advance or retard for each successive tooth along any one flute. It is therefore essential when operating on this latter form of cutter that the operative position of the tool be slightly advanced or retarded as the tool carriage moves longitudinally along the cutter. The compensating mechanism heretofore referred to and particularly shown in Figs. 12, 13 and 14 of the drawings is adapted to perform this function. Referring particularly to Figs. 2, 4, 12, 13 and 14, it will be seen that the shaft 56 which controls the tool in performing its relieving operations is driven from the high speed shaft 70 through the differential gearing 83 and the change speed mechanism 86. The differential gearing comprises a bevel gear 176 fast on shaft 70, two bevel gears rotatably mounted on a hub 177 keyed to the shaft 84 and a bevel gear 178 integral with a worm wheel 179 mounted loosely on the shaft 84. As illustrated, the bevel gear 17 8 and worm wheel 179 are adapted to be driven from the screw 92 through change speed gearing 180, shaft 181,- bevel gears 182 and worm shaft 183 having a worm thereon meshing with the worm wheel '17 9.

As above stated, when relieving cutters I having straight longitudinal flutes the angular starting position of the tool relative to the cutter is the same for each succes- "sive tooth along any one flute. During such operation no retarding or advancing movement of the tool is required and therefore the change speed gearing is disconnected from the screw, and the worm wheel 179 and bevel gear 178 are therefore held against rotation. Under such condition it will be seen that the rotation of shaft rotates the bevel gear 176 which rotates the bevel gears on the hub 177 over the stationary gear 178 whereby the hub 177 and shaft 84 are rotated in the same direction and at the same an ular speed as the shaft 70. The position 0 the tool relative to the angular position of the cutter or hob is therefore the same regardless of the position of the tool carriage along the cutter.

Vhen relieving cutters having flutes arranged spirally therein the cutting position of the tool is slightly retarded or advanced as the tool carriage moves longitudinally along the cutter to allow for the slightly different angular position of each successivetooth relative to the cutter. In operation, the bevel gear 178 is given a slight rotation from the tool carriage operating screw 92 as the carriage is advanced along the cutter, the direction of rotation and the speed of the gear 178 being controlled through the change speed gearing 180. It will be clear from Fig. 14: that the rotation of the shaft 84 and therefore the relieving operation of the tool relative to the rotation of the shaft 70 is varied directly by the rotation of gear 178. Also the gear 178 is operated synchronously with the longitudinal movement of the carriage since both are operated from the screw 92. It will therefore be seen that during the relieving operation of the tool, the tool is advanced or retarded synchronously with the longitudinal advancing movement of the carriage.

lVhat I claim is:

1. In a lathe, the combination of a work supporting and driving spindle, a drive shaft operatively connected to the spindle to rotate the latter at a reduced speed, a tool supporting carriage, a screw for moving the carriage longitudinally of the spindle, two shafts parallel with and adj acent the screw, means for driving one shaft relatively slowly from the spindle, means for driving the other shaft relatively fast from the drive shaft independently of the spindle, and change speed gearing adapted to operatively connect the screw to either of said shafts.

2. In a lathe, the combination of a work supporting and driving spindle, a drive shaft operatively connected to the spindle to rotate the latter at a reduced speed, a tool supporting carriage, a screw for moving the carriage longitudinally of the spindle, one end of the screw projecting outwardly of the lathe, two shafts substantially equally spaced from the said screw end and projecting outwardly of the lathe, means for driving one shaft relatively slowly from the spindle, means for driving the other shaft relatively fast from the drive shaft independently of the spindle, and change speed III the relieving operation of the tool, and

means whereby the screw may be driven either from the spindle or from the high dle speed shaft through other mechanism independently of the spindle.

4. In a relieving lathe, the combination of a work supporting and driving spindle, a tool-supporting carriage, a screw for moving the carriage longitudinally of the spina relatively high speed shaft for controlling the relieving operation of the too-l, and means including two shafts adjacent the screw and driven from the spindle and high speed shaft through other mechanism independently of the spindle respectively, whereby the screw may be driven either from the spindle or from the high speed shaft, the screw being adapted to be connected with either of the said shafts through change speed gearing.

. 5.In a lathe, the combination of a work supporting and driving spindle, a toolsupporting carria e, a screw for moving the carriage longitu 'nally of the spindle, a

relatively slow and a relatively fast screw driving means synchronously connected with the spindle, and an indexing mechanism adapted to be mounted on either of the said two means, the spindle and either of the said two means and the screw being adapted to be relatively indexed through the indexin mechanism.

6; 1%: a lathe, the combination of a work supporting and driving spindle, a tool-supporting carriage, a screw for moving the carriage longitudinally of the spindle, means comprising a relatively slow and a relatively fast shaft synchronously connected with the spindle and adjacent the screw, the screw being adapted to be connected with either of the said shafts through change speed gearing, a two-part indexing mechanism adapted tobe mounted on either of the said two shafts, one part being adapted to be operatively connected to the screw through the change speed gearing and the other part to the shaft on which it is mounted, and means for securing such parts together in any one of a plurality of relatively angular positions to relatively index the shaft-and screw.

7. In a lathe, the combination of a work supporting and driving spindle, a drive shaft operatively connected to the spindle to rotate the latter at a reducal speed, a toolsupporting carria a screw for moving the carriage longit dinally of the spindle,

means comprising two shafts adjacent the screw and driven from the spindle and drive shaft respectively whereby the screw may either be driven relatively slow from the spindle or relatively fast from the drive g, shaft, the screw being adapted to be connected With either of the said shafts through change speed gearing, a two-part indexing mechanism adapted to be mounted on either of the said two shafts, one part being adapted to be operatively connected to the screw through the change speed gearing and the other part to the shaft on which it is mounted, and a latch for securing such parts together in any one of a plurality of relatively angular positions to relatively index the shaft and screw.

8. In a relieving lathe, the combination of a work supporting and driving spindle, a tool holder, a shaft adapted to reciprocate the tool holder toward and from the work to efiect relieving, a synchronous operative connection between the shaft and spindle, a manually operable element, and means adapted to be operated by the element to disengage such connection and effect a relative rotative movement between the spindle and shaft.

9. In a relieving lathe, the combination of a work supporting and driving spindle, a tool holder, a shaft adapted to reciprocate the tool holder toward and from the work to effect relieving, a synchronous operative connection between the shaft and spindle, a manually operable element, means adapted to be operated by the element to disengage such connection and effect a relative rotative movement between the spindle and shaft, and a spring-pressed latch for holding the last named means in its engaged position.

10. In a relieving lathe, the combination of a work supporting and driving spindle, a tool holder, a shaft adapted to reciprocate the tool holder toward and from the work to effect relieving, a synchronous operative connection between the shaft and spindle, and means comprising a sliding gear and a hand wheel operatively connected thereto whereby such connection may be disengaged and a relative rotative movement effected between the spindle and shaft, the hand wheel beingadapted to effect both the disengaging movement and the rotative movement.

11. In a relieving lathe, the combination of a work supporting and driving spindle, a tool holder, a shaft adapted to reciprocate the tool holder toward and'from the work to effect relieving, a synchronous operative connection comprising aplurality of gears between the shaft and spindle, vone of such gears being mounted on a longitudinally adustable shaft whereby such gear may be disengaged from one of its companion gears, and a hand wheel on the shaft for shlftin the shaft and gear axially to the disengag position and for rotating the shaft and the gearing connected therewith wherebya relative rotative movement is efiected between the spindle and shaft.

12. In a tool feeding mechanism, the combination of a tool holder, a feed screw operatively connected thereto, a stop connected to the feed screw, screw rotating means frictionally connected to the stop, a worm wheel loosely mounted coaxially of the screw, a stop on the worm wheel in the path of movement of the first stop, and a worm engaging the worm wheel to place the second stop in any desired position relative to the first stop whereby to stop the feed of the tool at the desired point, the said frictional connection permitting the stopping of the screw though the screw rotating means continues to operate.

13. In a relieving lathe, the combination of means for holding and rotating a cutter, a tool carriage, a-tool holder mounted on the carriage, means for moving the tool holder toward and away from the cutter in timed relation to the rotation thereof, a device for giving the tool holder a feeding movement supplemental to the aforesaid normal movements, automatic means for operating the feeding device, means for preventing the operation of the feeding device by the said automatic means after feeding has taken place to a predetermined extent, and means including a shaft mounted in the carriage for adjusting the last named means to vary the tent of feed.

14. In a relieving lathe, the combination of means for holding and rotating a cutter, a tool carriage, a tool holder mounted on the carriage, means for moving the tool holder toward and away from the cutter in timed relation to the rotation thereof, a device for giving the tool holder a feeding movement supplemental to the aforesaid normal movements, automatic means for operating the feeding device, and means comprising a pair of stops for preventing the operation of the feeding device by the said automatic means after feeding has taken place to a predetermined extent, one stop being connected to the screw and the other stop being adjustably mounted in the path of movement of the first stop.

15. In a relieving lathe, the combination of means for holdlng and rotating a cutter, a tool carriage, a tool holder mounted on the carriage, means-for moving the tool vholder toward and away from the cutter in timed relation to the rotation thereof, a device for giving the tool holder a feeding movement supplemental to the aforesaid normal movements, automatic means for operating the feeding device, and means comprising a pair of stops for preventing the operation of the feeding device by the said automatic means after feeding has taken place to a predetermined extent, one stop being frictionally connected to the screw operating means and the other sto being adjustably mounted in the path 0 movement of the first stop.

16. In a relieving lathe, the combination of means for holding and rotating a cutter, a tool carriage, a tool holder mounted on the carriage, means for moving the tool holder toward and away from the cutter in timed relation to the rotation thereof, a device for giving the tool holder a feeding movement supplemental to the aforesaid normal movements, automatic means for operating the feeding device, means comprising a pair-of stops for preventing the operation of the feeding device b the said automatic means after feeding as taken place to a predetermined extent, one stop' being rigidly connected to the screw and frictionally connectedto the screw operating means and the other stop being adjustab y mounted in the path of movement of the first stop, and means removed from the stops and mounted on the carriage for adjustin the second stop.

17. n a relieving lathe, the combination of a work supporting and driving spindle, a tool-supporting carriage, a screw for moving the carriage longitudinally of the spindle, means for controlling the relieving operation of the tool, a compensating mechanism operatively connected with the screw and the relieving means and adapted to slightly retard or advance the relieving positlon of the tool as the tool carriage is moved longitudinally along the work, tool feeding mechanism adapted to automatically feed the tool intermittently at predetermined intervals in the rotation of the work, and means for rendering either of the said mechanisms operative or inoperalive.

18. In a relieving lathe, the combination of a work supporting and driving spindle, a tool-supporting carriage, a screw for moving the carriage longitudinall of the spindle, a relatively high speed s aft for controlling the relieving operation of the tool, a differential compensating mechanism operatively connected with the screw and the shaft and adapted to slightly retard or advance the relieving position of the tool as the tool carriage is .moved longitudinally along the work, tool feedin mechanism adapted to automatically fee the tool once during each rotation of the work, and

means for rendering either of the said mechanisms operative or inoperative.

19. In a relieving lathe, the combination of a work supporting and driving spindle, a tool-supporting carriage, a screw for moving the carriage longitudinall of the spindle, a relatively high speed s aft for controlling the relieveing operation of the tool, a differential compensating mechanism in the tool operating connection through the,

shaft, the screw being operatively connected to a portion of the differential mechanism, change gears for varying the amount of difl'erential l action of the compensating mechanism, the compensating mechanism being adapted to slightly retard or advance the relieving position of the tool as the tool carriage is moved longitudinally along the Work, tool feeding mechanism adapted to automatically feed the tool intermittently during the rotation of the'vvork, and means for rendering either of the said mechanisms operative or inoperative.

20. A tool support comprising the combination of a base, a plurality of bolts mounted in the base and projecting in a relatively parallel direction therefrom, and a tool-supporting block having a plurality of holes therein for receiving the said bolts, the block being adapted to be mounted on the base in any one of a plurality of angular positions.

21. A tool support comprising the com bination of a base, a, plurality of bolts mounted symmetrically on the-base and proj ecting in a relatively parallel direction v therefrom, and a tool-supporting block hav-.

ing a plurality of holes therein corresponding in number and relative location to the block having four holes therein bolts in the base, the block being adapted to be mounted on the base in as many angular positions as there are bolts in the base With each bolt entering a hole in the block.

22. A tool support comprising the combination of a base, four bolts mounted in the base and projecting in a relatively parallel direction therefrom, and a tool-supporting block having four holes therein corresponding in location to the bolts in the base, the block being adapted to be mounted on the base in any one of four relatively right angular positions with each bolt entering a hole in the block.

23. A tool support comprising the combination of a base, four bolts mounted in the base and allel direction therefrom, a-tool-supporting corresponding in location to the bolts in the base, the block being adapted to be mounted on the base in any one of four relatively right angular positions With each bolt entering a hole in the block, and a tool-securing strap adapted to clamp the tool in position on the block by means of tWo of the said bolts. a

In testimony whereof, I hereto affix my signature.

FRIEDERICH MuLLER.

projecting in a relatively par- 

